JP2000337475A - Torque transmitting mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torque transmitting mechanism superior in cooling effect and capable of surely executing the lock-up operation. SOLUTION: A frictional member 34 mounted between a lock-up piston 30 and a front cover 26 is provided with a groove 36 inclined in the direction opposite to the rotating direction of the frictional member 34 by a predetermined inclination angle θ, and not reaching an inner peripheral surface 34B of the frictional member 34. A through hole 40 penetrating the lock-up piston 30 is formed on a position corresponding to an inner end of the groove 36. The oil flows in a channel 38 in a lock-up state, and the frictional member 34, a front cover 26 and the lock-up piston 30 are cooled. As an outer peripheral side and an inner peripheral side of the frictional member 34 are separated by the frictional member 34, the pressure difference generated between the outer peripheral side and the inner peripheral side of the frictional member 34 can be kept at a constant value, and the load for pressing the lock-up piston 40 to the front cover 26 can be kept.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotational force transmitting mechanism that applies kinetic energy to a fluid by rotation of an input member, such as a fluid clutch or a torque converter, and rotates an output member by the kinetic energy.

[0002]

2. Description of the Related Art FIG. 10 shows a torque converter 110 used in combination with an automatic transmission of an automobile as an example of a conventional torque transmitting mechanism (see Japanese Patent Application Laid-Open No. 7-208577).

[0003] This torque converter 110 has a so-called lock-up clutch, and at the time of lock-up, a friction lining 114 held by a piston 112 is provided.
The (friction member) contacts the casing shell 116, and the piston 112 and the casing 118 are connected by frictional engagement, so that the piston 112 rotates without loss of torque.

Generally, in a fluid clutch, a torque converter, or the like having such a lock-up mechanism, in order to increase the transmission torque and to reduce the size of the device itself, a friction lining 114 and a casing shell 116 are required.
It is necessary to increase the frictional force with the contact and reduce the contact area. However, when the frictional force is increased or the contact area is reduced, the temperature rise of the casing shell 116 and the friction lining 114 due to the frictional work at the time of engagement increases. These members are rapidly deteriorated due to such a rise in temperature, and their life is shortened.

In order to prevent such a temperature rise, in this torque converter 110, as shown in FIGS. 11 to 14, a groove 120 penetrating the outer peripheral side and the inner peripheral side of the friction lining 114 is formed. By allowing the lubricating oil to flow through the inside 120, the friction lining 114 is cooled (so-called wet clutch).

However, since the lock-up mechanism ensures that the piston 112 is brought into contact with the casing shell 116 by the pressure difference between the outer peripheral side and the inner peripheral side of the friction lining 114, the groove 120 is simply formed in the friction lining 114. If it is provided and the outer peripheral side and the inner peripheral side communicate with each other, this pressure difference becomes small, and it is difficult to reliably perform lock-up. Therefore, in the torque converter 110, the throttle portion 122 is provided in a part of the flow path formed by the groove 120 to suppress a decrease in the pressure difference.

However, since the flow rate of the lubricating oil in the groove 120 depends on the cross-sectional area of the throttle portion 122, it is necessary to increase the cross-sectional area of the throttle portion 122 in order to increase the flow rate and enhance the cooling effect. Preferably, on the other hand, friction lining 11
In order to increase the pressure difference between the outer peripheral side and the inner peripheral side of 4,
It is preferable that the cross-sectional area of the narrowed portion 122 is small. Therefore, if the cooling effect is enhanced by increasing the cross-sectional area of the constricted portion 122, the pressure difference is reduced and the operation of the lock-up mechanism becomes difficult.

[0008]

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to provide a rotational force transmitting mechanism which has a high cooling effect and can reliably perform lock-up operation.

[0009]

According to a first aspect of the present invention, there is provided a rotational force transmitting mechanism for applying kinetic energy to a fluid by rotation of an input side member and rotating an output side member by the kinetic energy. A first rotating member that rotates integrally with the side member; and a second rotating member that rotates integrally with the output side member and receives the load from the fluid and approaches the first rotating member.
A rotating member, provided between the first rotating member and the second rotating member, and when the second rotating member approaches the first rotating member, it comes into contact with both the first rotating member and the second rotating member to cause friction A friction member for connecting the first rotating member and the second rotating member so as to rotate integrally with each other, and preventing a flow of the fluid between the outer peripheral side and the inner peripheral side to generate a pressure difference in the fluid; A flow path provided in the friction member, wherein the flow path allows a fluid to flow in or out from the outer periphery of the friction member in a state where the friction member is in contact with both the first rotation member and the second rotation member;
And a through-hole provided in the rotating member and capable of moving the fluid between the flow path and the back side of the second rotating member.

Accordingly, when the second rotating member approaches the first rotating member and the friction member comes into contact with both the first rotating member and the second rotating member, the first rotating member and the second rotating member are separated by friction. They are connected so as to rotate integrally. Thus, the input-side member and the output-side member are directly connected via the first rotating member, the friction member, and the second rotating member (lock-up operation). Further, in this state, the flow of the fluid between the outer peripheral side and the inner peripheral side of the friction member is blocked, and the pressure difference generated between the outer peripheral side and the inner peripheral side is maintained. Due to this pressure difference, the second
The rotating member is strongly pressed against the first rotating member, and the lock-up operation is reliably performed.

A flow path is provided in the friction member, and fluid can flow in or out from the outer peripheral side of the friction member in a state where the friction member is in contact with both the first rotating member and the second rotating member. Also, a through hole is formed in the second rotating member,
The fluid can be moved between the flow path and the back side of the second rotating member. The flow path and the through holes constitute a fluid recirculation as a whole, and the fluid can be continuously supplied to the inside of the friction member, so that the friction member, the first rotating member and the second rotating member are effectively cooled. be able to.

Further, the flow path does not communicate the outer peripheral side and the inner peripheral side of the friction member, and the outer peripheral side and the inner peripheral side are completely isolated by the friction member. Therefore, a large pressure difference is maintained between the outer peripheral side and the inner peripheral side of the friction member, and the lock-up operation can be reliably performed.

The flow of the fluid into or out of the flow path in the present invention is determined by one of the conditions such as the rotation direction of the friction member and the flow direction of the fluid. Absent. For example, when the torque transmission mechanism of the present invention is used as a torque converter of an automobile, fluid flows into the flow path from the outer peripheral side of the friction member when transmitting the driving force of the engine to the transmission, and the engine brake is applied. The fluid is set so as to flow out of the flow path to the outer peripheral side of the friction member when actuated. Of course, by changing the configuration of the flow path, the inflow and outflow of the fluid may be reversed at the time of driving and at the time of engine braking.

According to a second aspect of the present invention, in the first aspect of the invention, the flow path is inclined along the rotation direction of the rotation from the outer peripheral side to the inner peripheral side of the friction member. It is characterized by being formed in.

[0015] This facilitates the inflow and outflow of the fluid into and out of the flow path, so that the amount of fluid flowing through the flow path increases.
It is possible to further enhance the cooling effect.

According to a third aspect of the present invention, in the first or second aspect of the present invention, a plurality of the flow paths are provided at regular intervals along a circumferential direction of the friction member, and the through hole is provided. , A plurality of channels are provided corresponding to the flow paths.

As described above, by providing a plurality of flow paths, the cooling effect is enhanced as compared with the case where only one flow path is provided. In addition, since the flow paths are provided at regular intervals along the circumferential direction of the friction member, variations in the cooling effect of the friction member in the circumferential direction are reduced, and the friction member, the first rotating member, and the second rotating member are integrated. It is possible to cool in a similar manner.

[0018]

FIG. 1 shows a torque converter 10 used in combination with an automatic transmission of an automobile as a torque transmitting mechanism according to a first embodiment of the present invention.

The torque converter 10 has a casing 14 which rotates integrally with a drive shaft (not shown) which is an input side member. The drive shaft is also connected to a rotation shaft of an engine (not shown), and rotates by receiving the rotation force of the engine.

The casing 14 is filled with oil, and the pump impeller 16
And a turbine runner 18. The pump impeller 16 is connected to a drive shaft (not shown), and the turbine runner 18 is connected to a driven shaft 20. When the pump impeller 16 rotates together with the drive shaft, kinetic energy is given to oil to generate an oil flow. Gives further rotational torque to the turbine runner 18,
The driven shaft 20 rotates.

A stator 24 is rotatably provided between the pump impeller 16 and the turbine runner 18 via a one-way clutch 22. The oil exiting the turbine runner 18 flows along the stator 24 and strikes the pump impeller 16 again. As a result, the pump impeller 16 further receives rotational torque, so that torque transmission loss due to the oil flow is reduced.

The casing 14 includes a front cover 26 arranged on the engine side (not shown) (the left side in FIG. 1),
A casing shell 28 disposed on the automatic transmission side (right side in FIG. 1) also not shown.
, And these are integrally connected.

The turbine runner 18 and the front cover 2
6, a lock-up piston 30 that rotates integrally with the driven shaft 20 and the turbine runner 18 is provided. As shown in FIG. 2, a predetermined gap 32 is formed between a flange 26 </ b> A formed on the outer circumference of the front cover 26 and a flange 30 </ b> A formed on the outer circumference of the lockup piston 30. Pump impeller 1
A part of the oil flow generated by the rotation of
2 through the turbine runner 18 and the front cover 26
You can flow between.

In the vicinity of the outer periphery of the lock-up piston 30, a friction material 34 is attached to a surface facing the front cover 26. As can be seen from FIG. 2B, the friction material 34 is formed in a ring shape having a certain thickness. If the predetermined conditions for operating the lock-up are not satisfied, the friction material 34 and the front cover 26
When a certain condition is satisfied, a load from oil acts on the lock-up piston 30 to deform the lock-up piston 30 in a direction approaching the front cover 26. , FIG. 1, FIG. 2 (B)
As shown in FIG. 3 and FIG.
Pressed to 6. The frictional engagement between the friction material 34 and the front cover 26 causes the lock-up piston 3
0 rotates integrally with the front cover 26 (lock-up operation).

The friction member 34 comes into contact with and is pressed against the front cover 26 in this manner, so that the friction member 34 is pressed.
The outer peripheral side and the inner peripheral side are separated from each other, and a pressure difference occurs between these oils. As can be seen from FIG. 3, since this pressure difference acts as a load (pressing load) for pressing the lock-up piston 30 toward the front cover 26, the lock-up piston 30 is pressed more strongly toward the front cover 26, The frictional force between the friction material 34 and the front cover 26 increases.

The friction material 34 has a groove 36 having a substantially constant width penetrating the friction material 34 in the plate thickness direction.
A is formed from A to the inner circumference. The groove 36
Are formed at predetermined intervals along the circumferential direction of the friction material 34 (16 in the present embodiment). As can be seen from FIG. 3, in a state where the friction material 34 is in contact with the front cover 26, the groove 36, the front cover 26, and the lockup piston 30 allow the oil to flow into the flow path 3.
8 are configured. As shown in FIG. 2 (A), when the angle between the tangent line P of the outer peripheral surface 34A of the friction material 34 and the tangent line P is defined as an inclination angle, the groove 36 becomes closer to the inner periphery from the outer peripheral surface 34A. 2 (indicated by an arrow R in FIG. 2A) at a constant inclination angle θ. In this way, by inclining the groove 36, that is, the flow path 38, compared with the case where the flow path 38 is provided along the radial direction,
The rotation of the friction material 34 makes it easier for oil to flow into the flow path 38. If such a flow path 38 is formed, the groove 36 does not necessarily have to penetrate the friction material 34 in the plate thickness direction, and is formed, for example, only at the central portion in the plate thickness direction (that is, the groove 36 is formed). The friction material 34 is provided at the end in the thickness direction.
May be left).

As shown in FIG. 2A, the groove 36 has a predetermined length so as not to reach the inner peripheral surface 34B of the friction material 34. Is friction material 3
4 completely isolated. Thereby, the oil does not directly move on the outer peripheral side and the inner peripheral side of the friction material 34,
The pressure difference between them is maintained at a constant value without decreasing.

The lock-up piston 30 has a through hole 40 formed at a position corresponding to the inner end of the groove 36 so as to penetrate the lock-up piston 30 in the plate thickness direction. Channel 3
8 can flow out to the rear side (right side in FIGS. 2B and 3) of the lock-up piston 30 through the through-hole 40, and as a whole, the oil circulates in the casing 14 (return and return). Become).

Next, the torque converter 10 of the present embodiment
The operation of will be described.

If certain conditions for establishing the lock-up state are not satisfied, the lock-up piston 30
Are not deformed toward the front cover 26, and the friction material 34 is not in contact with the front cover 26. Therefore, the front cover 26 rotates separately from the lock-up piston 30, and the oil to which kinetic energy is given by the rotation of the drive shaft and the pump impeller 16 (not shown) further gives a rotational torque to the turbine runner 18. The driven shaft 20 rotates.

The above-mentioned constant condition is set to a desired condition depending on the relationship between the torque converter 10 itself and the running state of the vehicle provided with the torque converter 10. For example, this condition may be determined according to the vehicle speed of the automobile, and in consideration of other conditions, the flow of the oil is controlled via a control device or the like, so that the deformation of the lockup piston 30 is controlled. Is also good.

When the certain condition is satisfied, the lock-up piston 30 is deformed toward the front cover 26 by receiving a load from the oil flowing through the casing 14,
The friction material 34 contacts the front cover 26. Friction material 3
Reference numeral 4 frictionally engages with the front cover 26, and the lock-up piston 30 and the front cover 26 rotate integrally via the friction material 34.

The oil in the casing 14 passes through the gap 32 as shown by the arrow F in FIG.
And between the lock-up piston 30 and the flow path 38. The friction material 34 is used for the front cover 2.
The temperature tends to rise due to the friction with the friction material 6, but the oil flows through the friction material 34 as described above, so that a part of the heat of the friction material 34 is absorbed by the oil. The front cover 26 and the lock-up piston 30 are also cooled.

The oil that has become high temperature in the flow path 38 flows through the through hole 40 to the rear side of the lock-up piston 30. As a result, the oil circulates as reflux, so that the low-temperature oil cooled in the casing
6, the friction material 34, the front cover 26, and the lock-up piston 30 can be cooled more effectively.

The grooves 36 are formed obliquely at a constant inclination angle θ in consideration of the rotational direction (the direction of the arrow R) of the friction material 34. 38. Thereby, the flow path 38
The flow rate of the oil flowing through the inside is increased, and the flow rate of the oil per unit time is increased.
4. Front cover 26 and lock-up piston 30
Can be cooled.

FIG. 4 shows the amount of heat Q input to the friction material,
The relationship between the surface temperature T of the front cover and the case of the torque converter 10 of the present embodiment (solid line) and the case of the conventional torque converter without the groove 36 and the through-hole 40 (dashed line) are respectively shown. It is shown. As shown in FIG. 3, the surface temperature T is an average value measured at a predetermined measurement point M. As can be seen from this graph, in the torque converter 10 of the present embodiment, as compared with the conventional torque converter, regardless of the magnitude of the heat amount Q,
It can be seen that the surface temperature T of the front cover 26 has decreased by about 20 ° C.

Further, since a plurality of grooves 36 are formed, the total flow rate of oil is increased and the cooling effect is enhanced as compared with the case where only one groove 36 is formed. Further, since the plurality of grooves are formed at regular intervals in the circumferential direction of the friction material 34, the friction material 34, the front cover 26, and the lock-up piston 30 can be uniformly cooled in the circumferential direction.

The groove 36 does not reach the inner peripheral surface 34B of the friction material 34, and when the friction material 34 is pressed against the front cover 26, the outer peripheral side and the inner peripheral side of the friction material 34 As a result, the oil does not directly move on the outer peripheral side and the inner peripheral side of the friction material 34. Therefore, the pressure difference generated between the outer peripheral side and the inner peripheral side of the friction material 34 is maintained at a constant value without decreasing, and the load for pressing the lock-up piston 30 against the front cover 26 can be maintained at a predetermined value or more. Therefore, the lock-up state can be reliably maintained.

FIG. 5 shows a friction material 54 and a lock-up piston 50 according to a second embodiment of the present invention. The second embodiment differs from the first embodiment only in the configuration of the friction material 54 and the lock-up piston 50, and the other configurations are the same. Only 50 will be described, and the other description will be omitted.

In the friction material 54, instead of the groove, a substantially triangular concave portion 56 which is gradually narrowed from the outer peripheral surface 54A toward the inner periphery of the friction material 54 is formed in a front view. Considering the streamline V of the flow path 58 formed by the concave portion 56, the streamline V is inclined at a predetermined inclination angle θ with respect to the tangent line P. Also, as in the first embodiment,
A plurality of recesses 56 (eight in this embodiment) are formed at predetermined intervals along the circumferential direction of the friction material 54.

The lock-up piston 50 has a recess 56
At the position corresponding to the innermost corner, a through-hole 60 is formed to penetrate the lock-up piston 50 in the plate thickness direction.

In the second embodiment, by forming such a triangular recess 56, the cross-sectional area of the flow path 58 is increased on the inlet side of the flow path 58 (the outer peripheral side of the friction material 54). Therefore, even if the rotational angular velocity of the friction material 54 is low in the lock-up state, more oil can flow into the flow path 58 and the friction material 54 can be cooled effectively.

Further, since the outer peripheral side and the inner peripheral side of the friction material 54 are completely isolated in the lock-up state, the pressure difference generated between the outer peripheral side and the inner peripheral side of the friction material 54 is maintained at a constant value. hand,
The lock-up state can be reliably maintained.

FIG. 6 shows a friction material 74 and a lock-up piston 70 according to a third embodiment of the present invention. The third embodiment also differs from the first embodiment only in the configuration of the friction member 74 and the lock-up piston 70, and has the same other configuration. Only the piston 70 will be described, and the other description will be omitted.

In the friction material 74, the width and the length of the groove 76 are the same as those of the first embodiment. However, when viewed from the front, the groove 76 is inclined in the direction opposite to that of the first embodiment.
4 from the outer peripheral surface 74A toward the inner periphery.
4 is formed so as to be inclined at an inclination angle θ in the same direction as the rotation direction. Further, similarly to the first embodiment, a plurality of grooves (16 in the present embodiment) are formed at predetermined intervals along the circumferential direction of the friction material 74.

As in the first embodiment, a through hole 80 is formed in the lock-up piston 70 at a position corresponding to the inner end of the groove 76 so as to penetrate the lock-up piston 70 in the plate thickness direction.

In the third embodiment, since the groove 76 inclined in the opposite direction to that of the first embodiment is formed, the flow path 78 in which oil flows in the opposite direction of the first embodiment.
Is configured. That is, as shown by the arrow F2 in FIG.
0, and then the lock-up piston 7
0 and the front cover 26, and a gap 32
And circulates in the casing 14 (see FIG. 1).
Even with such an oil flow, the same cooling effect as in the first embodiment can be obtained.

Further, since the outer peripheral side and the inner peripheral side of the friction material 74 are completely isolated in a lock-up state, the pressure difference generated between the outer peripheral side and the inner peripheral side of the friction material 74 is maintained at a constant value. hand,
The lock-up state can be reliably maintained.

FIG. 8 shows a friction material 84 and a lock-up piston 30 according to a fourth embodiment of the present invention. In the fourth embodiment, only the configuration of the friction material 84 is different from that of the first embodiment, and the other configuration is the same. Therefore, only the friction material 84 will be described, and the other description will be omitted. Omitted. In the first to third embodiments, the friction material is shown in the drawing viewed from the lock-up piston 30 side. However, in the fourth embodiment, unlike the first to third embodiments, the friction material 84 is different. Are shown in the drawing viewed from the front cover 26 side. Therefore, the arrow R indicates the relative rotation direction when the friction material 84 is viewed from the front cover 26 side, which is the opposite direction to the first to third embodiments.

FIG. 9A shows a friction material 84 according to the fourth embodiment.
As shown in FIG. 5, the inner friction member 92 is attached to the lock-up piston 30 and the outer friction member 94 is attached to the front cover 28. The inner friction material 92 and the outer friction material 94 have the same thickness. In the lock-up state, as shown in FIG. 9B, the inner friction material 92 contacts the front cover 26 and the lock-up piston 30 Comes into contact with the outer friction material 94.

As can be seen from FIG. 8, the inner diameter R1 of the outer friction material 94 is larger than the outer diameter R2 of the inner friction material 92, and the outer friction material 94 is locked up.
An annular gap 90 is formed between the inner friction material 92 and the inner friction material 92.

As in the first embodiment, a plurality of (in the present embodiment, 16) grooves 86 inclined at a constant inclination angle θ are formed in the outer friction material 94 at predetermined intervals in the circumferential direction. I have. The groove 86 is formed so as to extend from the outer peripheral surface 94A of the outer friction material 94 to the inner peripheral surface 94B.
The oil that has flowed in from the outer peripheral side reaches the gap 90.

The lock-up piston 30 has a gap 90
A through hole 40 similar to that of the first embodiment is formed at a position corresponding to. Then, in the lock-up state, FIG.
As shown in (B), a channel 88 is formed by the groove 86 and the gap 90.

In the torque converter according to the fourth embodiment having the above-described structure, similarly to the first embodiment, in the lock-up state, the lock-up piston 30 receives the load from the oil flowing through the casing 14 and the front cover 30 26, the inner friction material 92 contacts the front cover 26 and the lock-up piston 3
Since 0 contacts the outer friction material 94, the lock-up piston 30 and the front cover 26 rotate integrally via the friction material 34.

The oil in the casing 14 is
As shown by an arrow F3 in (B), the fluid flows between the front cover 26 and the lock-up piston 30 through the gap 32 and further flows into the flow path 88, so that the friction material 84 is cooled, and the front cover is further cooled. 26 and the lock-up piston 30 are also cooled. Then, the oil that has become high temperature in the flow path 88 flows through the through-hole 40 to the back side of the lock-up piston 30 and circulates as a reflux.
The friction material 84, the front cover 26, and the lock-up piston 30 can be cooled more effectively.

Further, the outer peripheral side and the inner peripheral side of the frictional member 84 are completely separated by the inner frictional member 92 in a lock-up state, so that the pressure difference between the outer peripheral side and the inner peripheral side of the frictional member 84 is increased. (Strictly speaking, the pressure difference between the outer peripheral side and the inner peripheral side of the inner friction material 92) can be maintained at a constant value, and the lock-up state can be reliably maintained.

In the fourth embodiment, the outer friction material 94
Attached to the lock-up piston 30 and the inner friction material 9
2 may be attached to the front cover 26. Further, the number and positions of the through holes 40 are not particularly limited as long as the oil can be moved from the gap 90 to the back side of the lock-up piston 30 as described above.
In particular, when the outer friction material 94 is attached to the lock-up piston 30 and the inner friction material 92 is attached to the front cover 26, the through hole 40 is formed on the extension of the groove 86 in plan view, so that the oil The flow can be made smoother, and the cooling effect can be further enhanced.

As described above, in the torque converter (rotational force transmission mechanism) of the present invention, in any of the embodiments, the friction material is effectively cooled by the oil, and the outer peripheral side and the inner peripheral side of the friction material. The lock-up state can be reliably maintained by maintaining the pressure difference between the lock-up state and the lock-up state.

In the above description, a torque converter used in combination with an automatic transmission of an automobile has been described as an example of the torque transmitting mechanism of the present invention. However, the present invention is not limited to this. In short, a rotational force transmitting mechanism that connects the input side member and the output side member so as to rotate integrally via a friction member, and has a constant pressure difference between the outer peripheral side and the inner peripheral side of the friction member. Any rotational force transmission mechanism may be used as required. Therefore, a general fluid clutch may be used. In particular, the present invention is particularly effective in cooling a lock-up clutch in which a temperature rise due to frictional heat of a friction member or a so-called slip-control lock-up clutch in which a slip state continues.

The flow path of the present invention also includes the flow path 3 formed by the grooves 36, 76, 86 and the recess 56.
It is not limited to 8, 58, 78, and 88. In short, any configuration may be used as long as the oil can flow in or out from the outer peripheral side of the friction members 34, 54, 74, and 84 in the lock-up state. For example, the flow path may be bent at a middle portion in the longitudinal direction.

The friction member of the present invention does not necessarily need to be attached to the lock-up piston 30 or the front cover 26. For example, when the lock-up is not operated, the friction member does not contact both the front cover 26 and the lock-up piston. It may be rotatably mounted integrally with the driven shaft 20 so as to be positioned. The number of friction members is not limited to one, and a plurality of friction members may be arranged in the thickness direction to constitute the friction member of the present invention as a whole.

[0062]

As described above, according to the present invention, the fluid is provided on the friction member, and the fluid flows in or out from the outer peripheral side of the friction member while the friction member is in contact with both the first rotating member and the second rotating member. Since it has a flow path that can be used, and a through hole that is provided in the second rotating member and that enables fluid to move between the flow path and the back side of the second rotating member, the cooling effect is high, and the lock is high. The up operation can be performed reliably.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a torque converter according to a first embodiment of the present invention.

FIG. 2 shows a friction material, a lock-up piston and a front cover applied to the first embodiment of the present invention, and FIG.
1B is a front view, and FIG. 1B is a cross-sectional view taken along line II of FIG.

FIG. 3 is a view showing a friction material, a lock-up piston, and a front cover applied to the first embodiment of the present invention;
FIG. 2A is a sectional view taken along line II-II of FIG.

FIG. 4 is a graph showing the relationship between the amount of heat Q input to a friction material and the surface temperature T of the front cover in the case of the torque converter of the present embodiment and in the case of a conventional torque converter.

FIG. 5 is a front view showing a friction material applied to a second embodiment of the present invention.

FIG. 6 is a front view showing a friction material applied to a third embodiment of the present invention.

FIG. 7 is a sectional view taken along line VII-VII of FIG. 6, showing a friction material applied to a third embodiment of the present invention.

FIG. 8 is a front view showing a friction material and a lock-up piston applied to a fourth embodiment of the present invention.

FIG. 9 is a sectional view taken along line VII-VII of FIG. 6, showing a friction material and a lock-up piston applied to a fourth embodiment of the present invention. At the time of up operation.

FIG. 10 is a sectional view showing a conventional torque converter.

FIG. 11 is a sectional view partially showing a friction material applied to a conventional torque converter.

FIG. 12 is a cross-sectional view partially showing a friction material applied to a conventional torque converter.

FIG. 13 is a sectional view partially showing a friction material applied to a conventional torque converter.

FIG. 14 is a cross-sectional view partially showing a friction material applied to a conventional torque converter.

[Explanation of symbols]

 Reference Signs List 10 torque converter (rotational force transmission mechanism) 26 front cover (first rotating member) 30 lock-up piston (second rotating member) 34 friction material (friction member) 38 flow path 40 through hole 50 lock-up piston (second rotating member) ) 54 friction material (friction member) 58 flow path 70 lock-up piston (second rotating member) 74 friction material (friction member) 78 flow path 84 friction material (friction member) 88 flow path 92 inner friction material (friction material, friction) 94) Outer friction material (friction material, friction member)

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masanori Iriya 41-Cho, Yokomichi, Nagakute-cho, Aichi-gun, Aichi Prefecture Inside Toyota Central Research Laboratory, Inc. (72) Inventor Yuji Nagasawa Yuji Nagakute-cho, Nagakute-cho, Aichi-gun, Aichi Prefecture 41, Yokomichi, Toyota Central Research Laboratories Co., Ltd. (72) Inventor Hisashi Watanabe Hisashi Watanabe, 41, Nagakute-cho, Nagakute-cho, Aichi-gun, Aichi Prefecture 41 Toyota Chuo R & D Co., Ltd. (72) Inventor Masahiro Kojima 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation F-term (reference) 3J053 CA02 CA03 CB22 FB02 FC10

Claims (3)

[Claims] 1. A rotating force transmitting mechanism that applies kinetic energy to a fluid by rotation of an input side member and rotates an output side member by the kinetic energy, wherein a first rotating member that rotates integrally with the input side member; A second rotating member that rotates integrally with the output-side member and receives a load from the fluid and approaches the first rotating member; a second rotating member provided between the first rotating member and the second rotating member; When the two rotating members approach the first rotating member, the two rotating members come into contact with both the first rotating member and the second rotating member, and the first rotating member contacts the first rotating member.
A friction member that connects the rotating member and the second rotating member so as to rotate integrally, and that prevents a flow of the fluid between the outer peripheral side and the inner peripheral side to generate a pressure difference in the fluid; A flow path provided so that a fluid can flow in or out from a friction member outer peripheral side in a state where the friction member is in contact with both the first rotation member and the second rotation member; And a through-hole that allows the fluid to move between the flow path and the back side of the second rotating member. 2. The method according to claim 1, wherein the flow path is formed so as to be inclined along the rotation direction of the rotation from the outer peripheral side to the inner peripheral side of the friction member.
2. The torque transmission mechanism according to 1. 3. A plurality of the flow paths are provided at regular intervals along a circumferential direction of the friction member, and a plurality of the through holes are provided corresponding to the flow paths. The torque transmission mechanism according to claim 1 or 2.